外文翻译--双曲柄环板式针摆行星传动装置的传动效率分析

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中英文文献翻译—动力传动技术难点分析

附录APower transmission technology difficulty analysis1 And power system working characteristicsElectric vehicle has the advantages mainly in the following aspects:(1)Compared with the same kind of car engine emission reduction.(2) The motor as auxiliary power, to make the engine can play in good conditions, the efficiency of work and through the recycling braking energy, improve the vehicle's fuel economy.(3) By decrease engine load reduces the noise.(4) Transformed at present only gas stations, does not need to invest in new fuel loading.2, Planet row the characteristic of structure series(1) The engine is always in the best condition driving generators, so high efficiency, energy saving effect, have certain emissions, reduce pollution and low;(2) Installed the engine-generator, flowing energy feed to the traction motor, compared with the electric car trip mileage improved significantly;(3) Control system function, structure is simple, especially the operation control only generator according to the storage battery charging and discharging state decided to power or stopped.3. Selection strategy3.1 A motor vehicles in China for the development of has just started, to speed up the development of the hybrid products in China, the research and use for reference foreign results is very necessary. Power system selection in hybrid developing in a position of importance. Because of the different control strategy is based on a hybrid drive system for making and optimization. Can say power system structure types of the option to decide the hybrid of research and development, the relationship between key development progress and product the level, is the most important of HEV development and the key step. So the development must be in deep research of careful analysis and weigh the advantages and disadvantages, and on the basis of the structure of the power system type make discreet choice. In the development of comprehensive coordination performance should be advanced,technical complexity and costs and maintenance cost, according to the relationship between the use of cars conditions and their technical conditions, choose to meet the performance of both must be advanced, and not beyond the current technology conditions, and the price and maintenance costs for market acceptable to the power system type. Therefore, it is necessary to consider the following factors: (1) Motor drive power system based on particular condition commonly carry on the design. This is because most of the power system is more sensitive to working conditions, different operating conditions of the performance difference is very big, only in specific conditions to be fully low oil consumption, low emission advantages. (2) Different types of hybrid differences between performance is very clear, in the selection of the power system must be caused by the difference between performance to structure sufficient attention. If demand is high for acceleration performance, it is necessary to choose equipped with the structure of peak power regulator type; If the economy too hard, tandem, we cannot be the right choice. (3) The technical conditions, in addition to developing the conditions and power outside, still include industrial base. Stressed because of some common industrial base of power system in China, the components of the product level can not meet the requirements or still cannot production. In the actual product development will always have a certain schedule, if the technology conditions cannot be, it will be difficult to guarantee for achieving the development plan. Necessary to explore for his technical conditions especially industrial base of hybrid structure types, advocate structure innovation. (4)Open power system is to point to the need to further develop the space. Product performance is a gradually perfect process, the same development work might not one pace reachs the designated position, also need to have been the perfect. In the specific development work should be followed from the simple to the complex, from easy to difficult train of thought, to choose the technical conditions of the low required appropriate simple structure, development.(5) The structure of the power system of hybrid cost impact, this is because different types of power system for the kinds of components, the quantity and the performance requirements the difference is very big. And the kinds of components, the quantity and the performance index is the effect of the main factors of hybrid costs. Selection should also consider the use and maintenance costs, the more complex structure, the higher failure rate, use and maintenance cost is higher. Price and maintenance expenses directly related to the industrialization of HEV, if can't industrialization, can provide the necessary for further development of the capital, it will be difficult to promote and raisingthe level of technology to improve the performance of. In fact, the fine performance but because the price too high to commercialization, and even forced to give up the development of HEV examples not rarely seen, we should not repeat it.In view of our country at present the city's air pollution problems and oil shortages are very serious, and the technological basis of weak, preference hybrid system should be relatively simple structure, applicable to general city mode of the structure and the working condition between the cities series of parallel structure, and to buses and cars as a key development targets.It a: a hybrid car engine starting on and off, make frequent driving system and accessories (such as air conditioning and power steering, etc) of power management is complicated, so need advanced detection and control system; The existing to heat engine primarily hybrid unit in the fuel into YouYongGong at the same time, needs to improve the efficiency of conversion, and also to meet strict emission standard.Second: energy storage device (battery) to have higher than power, to meet the car accelerated and climbing to the need of high power when; At the same time, energy storage device must use heat control management, want to have higher than energy, long service life and low production cost.Third: must reduce the size of the power electronics device, reduce the quality and reduce production cost.Its 4: need to build a more advanced driving system mathematical model (including static and dynamic), is this the computer simulation and analysis of the foundation.Its 5: make perfect hybrid cars of relevant standards and regulations, for hybrid cars, which laid the foundation of the market.3.2 Electric drive system and car accessoriesTo make a hybrid car of the power, economy, comfort, safety and convenience to consumers can acceptable level, there must be efficient and economic power drive system and car accessories. However, the system of some components in the traditional car without a corresponding parts, so need to development design. In development at the same time, want to consider the system synthesis performance, costs and maintenance performance.1) Motor in a hybrid car, motor is the role of the generator or energy storage device provide electrical energy into mechanical energy is used to drive the wheels. And the traditional automobile different is, motor speed can provide in full, and engine torque must be to waituntil "mad" can only output loaded with torque. This makes hybrid cars have excellent starting and accelerating performance. In addition, used for a hybrid car motor must have good controllability and fault tolerance, and low noise, high efficiency, and is not sensitive to the voltage fluctuations and performance.Used for a hybrid car motor type has ac induction motor, permanent magnet motor and switched reluctance motor. At present the typical is ac induction motor, but this kind of motor are born is difficult to solve the contradiction between power and efficiency. Therefore, we need to study out can be used for hybrid cars, have higher efficiency and power density of permanent magnet motor, switched reluctance motor, and other advanced motor, to replace current use of ac induction motor. At the same time for the motor control method and the cooling system research also should go further.2)Regenerative braking, this kind of hybrid cars can recycle braking energy consumption part of. When a hybrid car brake, motor, generator, using cars into the kinetic energy to produce electricity, and can be stored in battery in it for later. In hybrid cars, there are many form of energy can be used as the regenerative braking energy storage device, such as high-speed flywheel, super capacitor, elastic device and all kinds of thermal system, etc. Of course, the traditional friction braking is necessary, so you need to consider how to two sets of braking equipment reasonable use, reasonable, and the problems of control. Braking, the electronic control system of the regenerative braking and friction braking system at the same time, the braking performance will be improved.3) Car accessories, any style of car to get consumers and all must consider the car comfort. The automobile air-conditioning accessories can improve the car of comfort, but energy use is very big, if not reduce the load, they will be for the automobile fuel economy have a huge impact. So, whether in the car at the same time, improve the comfort to improve fuel economy is at present to innovation of research. Traditional bus attachments system on the engine design, not for hybrid cars drive system. For example, the traditional automobile accessories (such as air condition, power steering, etc) by the engine drive, but because the hybrid car engines are not always work, need to design and production can the independent powered accessories. Be like again, because a hybrid car engine frequently starting and close, make its drive system and accessories for the power management complicated, need to have a more advanced monitoring and control system.3.3 A hybrid car simulation technologyIn the research and development of a hybrid car components and choose the best structure, need to design and maker can quickly reduce research scope, find technical breakthrough. Technical scheme selection stages, in the system the choice, can rely on efficient modeling tools computer, through the alternate use of candidate subsystems simulation, so as to find the best solutions. Computer models for each candidate subsystem provides a detailed specifications and design parameters, and convenient to the designer's work, but also to make model for designing and manufacturing engineering target and plan.Now, the responsible for electric cars and hybrid vehicles standards and regulations is the organization of the international electrotechnical commission (IEC), the international organization for standardization (ISO), the American auto engineers association (SAE), etc. For our country, because of hybrid cars are already in the experimental stage, and all the standards work should begin corresponding. For future will appear DuoZhong driving car coexistence, car standards will also need to consider the traditional automobile, hybrid cars and pure electric vehicle the comparability between universality and.附录B动力传动技术难点分析1、动力系统工作特点动力汽车所具备的优点主要表现在以下几个方面：(1)与同类发动机车型相比, 排放降低。

双曲柄环板式针摆行星传动效率分析

双曲柄环板式针摆行星传动效率分析
李欣;何卫东;李力行
【期刊名称】《大连交通大学学报》
【年(卷),期】2005(026)001
【摘要】应用行星轮系传动效率的通用计算机公式,推导出了双曲柄环板式针摆行星传动的传动效率计算公式.为了证明其理论的正确性,又进行了实验研究.样机效率试验结果与计算结果基本符合.试验结果证明,这种新型传动不仅具有高的承载能力,还有高的传动效率.
【总页数】4页(P11-14)
【作者】李欣;何卫东;李力行
【作者单位】马里兰大学,美国,马里兰;大连交通大学,机械工程学院,辽宁,大
连,116028;大连交通大学,机械工程学院,辽宁,大连,116028
【正文语种】中文
【中图分类】TH132.332
【相关文献】
1.三齿轮联动双曲柄环板式针摆行星传动中针摆传动误差分析的新思路 [J], 何卫东;刘鹏
2.双曲柄环板式针摆行星传动中平行四杆机构运动性能分析 [J], 孙涛;葛宰林;何卫东
3.双曲柄环板式针摆行星传动的参数优化 [J], 何卫东;王善梅;李力行
4.三齿轮联动双曲柄四环板式针摆行星传动的动力学研究 [J], 鲍君华;何卫东
5.双曲柄环板式针摆行星传动降低振动与噪声的优化设计与试验 [J], 何卫东;李欣;李力行;闻邦椿
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外文翻译

双曲柄环板式针摆线齿轮行星传动的动态制定和分析关键词：机械传动；针摆传动；双曲柄环板式针摆线齿轮行星传动；动力分析；集总参数法摘要假设环板和齿轮箱作为刚体,考虑臂轴承的影响和支持轴承的刚度,变形齿轮的啮合,论文构建了一个双曲柄环板式针摆线齿轮行星传动的动态模型,通过程序计算了渐开线齿轮和销摆线齿轮的啮合刚度,根据牛顿第二定律,一个33自由度动力学模型包括输入和输出轴，双渐开线齿轮和齿轮箱,由集总参数法得到了固有频率和振动特性系统与弯曲和扭转耦合工况,计算结果表明,当输入轴在1500 r / min时，在600 - 800赫兹和一些其他频段的系统容易引起共振,这也是相应的原型振动试验。

对于第一个原型具有明显的振动和噪声的问题,改善的方法就是加强齿轮箱刚度,增加第一传动比和放大输出轴刚度。

理论分析表明,该措施可以更好的降低这种新型传动的振动和噪声。

简介1 输出轴 2摆线 3内侧环形板（链接）图2 内部结构3′内侧环形板（链接） 4曲轴5从动齿轮 6传动齿轮 7输入轴8从动齿轮图1 双曲柄环板式针摆行星传动双曲柄环板式针摆行星齿轮传动是一种新型传动，它的创新发展基于传统的针摆行星齿轮驱动器[ 1，2 ]，其工作原理见图1，内结构见图2。

它不仅有销摆线齿轮行星传动具有的许多优点，如体积小，传动比范围大，使用硬齿面齿轮的齿，多齿啮合，其更大的承载能力，更高的传输效率和更流畅的操作，也有许多其他优点，如臂轴承放在外面，摆线齿轮轴承的径向尺寸已经不再限制，获得较高的承载能力。

由于历史短，特殊结构和工作原理，很少有对这种新型传动的详细的动力学研究，参考[ 3，7 ]阐述RV减速器的动态制定的理论，这也一种针摆线齿轮行星减速器，参考8详细介绍了RV减速器的动态制定及分析。

考虑啮合刚度的变化对摆线针的限制，论文的重点是用集总参数法对该减速器进行制定和分析，该轴承的刚度计算可以看参考9，啮合刚度的计算可以看参考[ 8，10 ]。

机械设计名词术语3

输出轴output shaft输入构件input link数学模型mathematic model双滑块机构double-slider mechanism，ellipsograph双列轴承double row bearing双曲柄机构double crank mechanism双曲面齿轮hyperboloid gear双头螺柱studs双万向联轴节constant-velocity （or double）universal joint 双向推力轴承double-direction thrust bearing双摇杆机构double rocker mechanism双转块机构Oldham coupling瞬心instantaneous center顺时针clockwise死点dead point四杆机构four-bar linkage松边slack-side速度velocity速度波动speed fluctuation速度不均匀（波动）系数coefficient of speed fluctuation速度曲线velocity diagram速度瞬心instantaneous center of velocity塔轮step pulley踏板pedal台钳、虎钳vice太阳轮sun gear套筒sleeve特殊运动链special kinematic chain特性characteristics梯形螺纹acme thread form替代机构equivalent mechanism铁磁流体密封ferrofluid seal停车阶段stopping phase停歇dwell同步带synchronous belt同步带传动synchronous belt drive凸的，凸面体convex凸轮cam凸轮倒置机构inverse cam mechanism 凸轮机构cam ，cam mechanism凸轮廓线cam profile凸轮廓线绘制layout of cam profile凸轮理论廓线pitch curve凸缘联轴器flange coupling图册、图谱atlas图解法graphical method推程rise推力球轴承thrust ball bearing推力轴承thrust bearing退刀槽tool withdrawal groove退火anneal陀螺仪gyroscope外齿轮external gear外力external force外圈outer ring外形尺寸boundary dimension弯矩bending moment弯曲应力beading stress万向联轴器Hooks coupling universal coupling 腕部wrist网上设计on-net design，OND往复式密封reciprocating seal往复移动reciprocating motion微动螺旋机构differential screw mechanism位移displacement位移曲线displacement diagram位姿pose ，position and orientation稳定运转阶段steady motion period稳健设计robust design蜗杆worm蜗杆传动机构worm gearing蜗杆头数number of threads蜗杆蜗轮机构worm and worm gear蜗杆形凸轮步进机构worm cam interval mechanism 蜗杆旋向hands of worm蜗杆直径系数diametral quotient蜗轮worm gear涡圈形盘簧power spring无级变速装置stepless speed changes devices无穷大infinite系杆crank arm，planet carrier细牙螺纹fine threads现场平衡field balancing相对间隙relative gap相对速度relative velocity相对运动relative motion橡胶弹簧balata spring橡皮泥plasticine向心力centrifugal force向心轴承radial bearing象限quadrant销pin消耗consumption小齿轮pinion小径minor diameter校正平面correcting plane斜齿轮的当量直齿轮equivalent spur gear of the helical gear 斜齿圆柱齿轮helical gear斜键、钩头楔键taper key谐波齿轮harmonic gear。

曲柄摇臂机构设计外文翻译文献

曲柄摇臂机构设计外文翻译文献(文档含中英文对照即英文原文和中文翻译)认识曲柄摇臂机构设计的最优传动方法摘要：一种曲柄摇臂机构设计的最优传动的方法被提出。

这种优化组合设计被用来找出最优的传递参数。

得出最优传递图。

在图中，在极小的传动角度之间, 滑移速度变化系数，摇臂的摆动角度和杆的长度被直观地显示。

这是这种方法拥有的主要特征。

根据指定的要求，它将传动角度之下的最优传动参数直接地表达在图上。

通过这种方法，机械传动的特性能用以获取最优传动效果。

特别是，这种方法是简单和实用的。

关键词:曲柄摇臂机构最优传动角度滑移速度变化系数引言由曲柄摇臂机构设计的常规方法, 在各种各样的参量之间很难找出优化组合的最优传动。

通过本文介绍的图面设计方法可以帮助达到这个目的。

在指定的情况下，通过观查设计图面, 我们就能得到每个参量和另外一个曲柄摇臂机构设计之间的联系。

由因认识最优传动。

具体的设计的理论和方法，以及它们各自的应用事例将在以下介绍。

1 优化传动设计的建立优化传动的设计一直是设计师改进传输效率和追求产量的最重要的索引的当中一个。

曲柄摇臂机构被广泛应用在机械传动中。

如何改进工作效率和减少多余的功率损失直接地与滑移速度变化系数，摇臂的摆动角度和曲柄摇臂的比率有关系。

这些参数的合理组合采用对机械效率和产量有重要作用, 这些主要体现在极小的传输角度上。

认识机械优化传动目的是找到极小的传输角度的最大值。

设计参数是适度地减少限制而且分开的合理优化方法的结合。

因此，完全限制领域的优化传动建立了。

以下步骤被采用在通常的设计方法。

首先，测量出摇臂的长度3l 和摇臂的摆动角度ϕ的初始值。

然后滑移速度变化系数K 的值被定在允许的范围内。

同时，曲柄固定的铰接座标A 可能被认为是任意值K 。

1.1 曲柄摇臂机构杆的长度由图Fig.1，左弧G C 2是点A 被允许的领域。

点A 的座标的选择从点2C 到点G 。

点A 的座标是02h y y c A -= (1)22A A y R x -= (2)当0h ，高度，在range(0 ，H ) 被逐渐增加。

双电机驱动双曲柄四环板针摆行星减速器参数化设计解读

双电机驱动双曲柄四环板针摆行星减速器参数化设计通过对双电机驱动和三齿轮联动两种形式双曲柄四环板针摆行星减速器样机进行的各种动态响应优化设计及试验研究后得出:前者的各方面性能指标均已满足国家对相关产品的质量要求,而三齿轮联动形式的样机还需进一步改进。

双电机驱动式减速器将有机会广泛应用于各类机械领域,因而有必要实现其系列化设计。

为避免系列化设计过程中大量重复性工作、提高设计效率,需要实现减速器零件工程图的参数化绘制。

由于各种形式双曲柄环板减速器样机中大量零件的结构都是相同的,所以此工作也有助于提高相关形式样机的优化改进设计的效率。

因为传统的CAD软件不支持参数化设计技术,本论文选择了参数化设计技术和数据库技术方面比较成熟的三维CAD软件Pro/ENGINEER及其二次开发包Pro/TOOLKIT作为实现工具,通过对零件三维模型的参数化设计实现对零件工程图的参数化绘制。

论文主要做了以下三方面工作:首先,根据参数化设计的主要思想和实质分析Pro/ENGINEER模型参数化设计的实质,在其交互模式下创建减速器所有零件的参数化三维模型样板,利用“参数”对话框按照不同的原则设置标准件和非标准件的用户参数,并通过“关系”对话框设置模型用户参数和系统建模参数之间的关系,实现用户参数对模型的驱动。

其次,为能够实现对复杂零件模型的参数化设计,借助于VC 平台和Pro/TOOLKIT开发包编写了能够运行于Pro/ENGINEER系统、并以其系统菜单形式控制的模型参数化设计界面程序。

图形用户界面技术极大地改善了模型参数信息的表达能力,解决了Pro/E系统“参数”对话框对模型参数表达能力有限的瓶颈问题,从而可以对任意复杂模型进行参数化设计。

最后,通过系统配置文件Config.pro和dtl格式的工程图配置文件设置Pro/ENGINEER绘图环境,并将其应用于按照公制标准创建的工程图模板文件中,熟练应用其工程图创建和工程信息标注的各种技巧,为前面创建的参数化零件模型创建尽可能满足国家标准要求的工程图。

(完整版)机械类外文文献翻译

文献翻译英文原文：NOVEL METHOD OF REALIZING THE OPTIMAL TRANSMISSION OF THE CRANK-AND-ROCKER MECHANISM DESIGN Abstract: A novel method of realizing the optimal transmission of the crank-and-rocker mechanism is presented. The optimal combination design is made by finding the related optimal transmission parameters. The diagram of the optimal transmission is drawn. In the diagram, the relation among minimum transmission angle, the coefficient of travel speed variation, the oscillating angle of the rocker and the length of the bars is shown, concisely, conveniently and directly. The method possesses the main characteristic. That it is to achieve the optimal transmission parameters under the transmission angle by directly choosing in the diagram, according to the given requirements. The characteristics of the mechanical transmission can be improved to gain the optimal transmission effect by the method. Especially, the method is simple and convenient in practical use.Keywords：Crank-and-rocker mechanism, Optimal transmission angle, Coefficient of travel speed variationINTRODUCTIONBy conventional method of the crank-and-rocker design, it is very difficult to realize the optimal combination between the various parameters for optimal transmission. The figure-table design method introduced in this paper can help achieve this goal. With given conditions, we can, by only consulting the designing figures and tables, get the relations between every parameter and another of the designed crank-and-rocker mechanism. Thus the optimal transmission can be realized.The concerned designing theory and method, as well as the real cases of its application will be introduced later respectively.1ESTABLISHMENT OF DIAGRAM FOR OPTIMAL TRANSMISSION DESIGNIt is always one of the most important indexes that designers pursue to improve the efficiency and property of the transmission. The crank-and-rocker mechanism is widely used in the mechanical transmission. How to improve work ability and reduce unnecessary power losses is directly related to the coefficient of travel speed variation, the oscillating angle of the rocker and the ratio of the crank and rocker. The reasonable combination of these parameters takes an important effect on the efficiency and property of the mechanism, which mainly indicates in the evaluation of the minimum transmission angle.The aim realizing the optimal transmission of the mechanism is how to find themaximum of the minimum transmission angle. The design parameters are reasonably combined by the method of lessening constraints gradually and optimizing separately. Consequently, the complete constraint field realizing the optimal transmission is established.The following steps are taken in the usual design method. Firstly, the initial values of the length of rocker 3l and the oscillating angle of rocker ϕ are given. Then the value of the coefficient of travel speed variation K is chosen in the permitted range. Meanwhile, the coordinate of the fixed hinge of crank A possibly realized is calculated corresponding to value K .1.1 Length of bars of crank and rocker mechanismAs shown in Fig.1, left arc G C 2 is the permitted field of point A . Thecoordinates of point A are chosen by small step from point 2C to point G .The coordinates of point A are 02h y y c A -= (1)22A A y R x -= (2)where 0h , the step, is increased by small increment within range(0,H ). If the smaller the chosen step is, the higher the computational precision will be. R is the radius of the design circle. d is the distance from 2C to G .2cos )2cos(22cos 33ϕθϕϕ⎥⎦⎤⎢⎣⎡--+=l R l d (3) Calculating the length of arc 1AC and 2AC , the length of the bars of themechanism corresponding to point A is obtained [1,2].1.2 Minimum transmission angle min γMinimum transmission angle min γ(see Fig.2) is determined by the equations [3]322142322min 2)(cos l l l l l l --+=γ (4) 322142322max 2)(cos l l l l l l +-+=γ (5) max min180γγ-︒=' (6) where 1l ——Length of crank(mm)2l ——Length of connecting bar(mm)3l ——Length of rocker(mm)4l ——Length of machine frame(mm)Firstly, we choose minimum comparing min γ with minγ'. And then we record all values of min γ greater than or equal to ︒40 and choose the maximum of them.Secondly, we find the maximum of min γ corresponding to any oscillating angle ϕ which is chosen by small step in the permitted range (maximum of min γ is different oscillating angle ϕ and the coefficient of travel speed variation K ).Finally, we change the length of rockerl by small step similarly. Thus we3γcorresponding to the different length of bars, may obtain the maximum ofmindifferent oscillating angle ϕand the coefficient of travel speed variation K.Fig.3 is accomplished from Table for the purpose of diagram design.It is worth pointing out that whatever the length of rocker 3l is evaluated, the location that the maximum of min γ arises is only related to the ratio of the length of rocker and the length of machine frame 3l /4l , while independent of 3l .2 DESIGN METHOD2.1 Realizing the optimal transmission design given the coefficient of travelspeed variation and the maximum oscillating angle of the rockerThe design procedure is as follows.(1) According to given K and ϕ, taken account to the formula the extreme included angle θ is found. The corresponding ratio of the length of bars 3l /4l is obtained consulting Fig.3.︒⨯+-=18011K K θ (7) (2) Choose the length of rocker 3l according to the work requirement, the length of the machine frame is obtained from the ratio 3l /4l .(3) Choose the centre of fixed hinge D as the vertex arbitrarily, and plot an isosceles triangle, the side of which is equal to the length of rocker 3l (see Fig.4), andϕ=∠21DC C . Then plot 212C C M C ⊥, draw N C 1, and make angleθ-︒=∠9012N C C . Thus the point of intersection of M C 2 and N C 1 is gained. Finally, draw the circumcircle of triangle 21C PC ∆.(4) Plot an arc with point D as the centre of the circle, 4l as the radius. The arc intersections arc G C 2 at point A . Point A is just the centre of the fixed hinge of the crank.Therefore, from the length of the crank2/)(211AC AC l -= (8)and the length of the connecting bar112l AC l -= (9)we will obtain the crank and rocker mechanism consisted of 1l , 2l , 3l , and 4l .Thus the optimal transmission property is realized under given conditions.2.2 Realizing the optimal transmission design given the length of the rocker (or the length of the machine frame) and the coefficient of travel speed variationWe take the following steps.(1) The appropriate ratio of the bars 3l /4l can be chosen according to given K . Furthermore, we find the length of machine frame 4l (the length of rocker 3l ).(2) The corresponding oscillating angle of the rocker can be obtained consulting Fig.3. And we calculate the extreme included angle θ.Then repeat (3) and (4) in section 2.13 DESIGN EXAMPLEThe known conditions are that the coefficient of travel speed variation1818.1=K and maximum oscillating angle ︒=40ϕ. The crankandrockermechanism realizing the optimal transmission is designed by the diagram solution method presented above.First, with Eq.(7), we can calculate the extreme included angle ︒=15θ. Then, we find 93.0/43=l l consulting Fig.3 according to the values of θ and ϕ.If evaluate 503=l mm, then we will obtain 76.5393.0/504==l mm. Next, draw sketch(omitted).As result, the length of bars is 161=l mm,462=l mm,503=l mm,76.534=l mm.The minimum transmission angle is︒=--+=3698.462)(arccos 322142322min l l l l l l γ The results obtained by computer are 2227.161=l mm, 5093.442=l mm, 0000.503=l mm, 8986.534=l mm.Provided that the figure design is carried under the condition of the Auto CAD circumstances, very precise design results can be achieved.4 CONCLUSIONSA novel approach of diagram solution can realize the optimal transmission of the crank-and-rocker mechanism. The method is simple and convenient in the practical use. In conventional design of mechanism, taking 0.1 mm as the value of effective the precision of the component sizes will be enough.译文：认识曲柄摇臂机构设计的最优传动方法摘要：一种曲柄摇臂机构设计的最优传动的方法被提出。

双曲柄双摆线行星传动的力分析与效率计算_胡来瑢

dow n test, the new scheme embodied a co mparativ ely go od speed g ov erning pro per ty. Key words: alternating curr ent moto r; planetary mag net ic par ticle clutch; step - less speed go verning Fig 5 T ab 1 Ref 4 / Jix ie Sheji0 4506
第 22 卷第 3 期 2 005年3月
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JO U RN A L O F M ACH IN E D ESIG N
V ol. 22 M ar.
N o. 3 2005
双曲柄双摆线行星传动的力分析与效率计算
胡来王容1 , 朱敬成2 , 吴红兵1
( 1. 湖北工业大学机械工程学院 , 湖北武汉 430068; 2. 郑州煤矿机械厂, 河南郑州 450007)
图2
双摆线齿轮廓间的啮合作用力
Abstract: By means of the study o n wo rking character istics of magnetic part icle clutch, the planetar y- g ear ed special pur posed magnetic part icle clutch was desig ned. T he new scheme of realizing step less speed r egulat ion for t he combinatio n o f al ter nat ing curr ent moto r and special purposed magnetic particle clutch w as put for war d. T hro ug h analytical calculatio n, shake -

双驱动双曲柄四环板针摆行星传动性能的研究的开题报告

双驱动双曲柄四环板针摆行星传动性能的研究的开题报告题目：双驱动双曲柄四环板针摆行星传动性能的研究研究目的：针对行星传动领域中传动效率、承载能力等问题，探究双驱动双曲柄四环板针摆行星传动的性能，并进行仿真与实验验证，为该领域的进一步发展提供技术支持。

研究内容：1. 双驱动双曲柄四环板针摆行星传动的设计原理及结构组成2. 基于ADAMS软件建立双驱动双曲柄四环板针摆行星传动模型，并进行运动学仿真分析3. 计算双驱动双曲柄四环板针摆行星传动的传动效率、承载能力等参数，并进行对比分析优缺点4. 制作双驱动双曲柄四环板针摆行星传动的实物，进行实验验证并对实验结果进行分析5. 就双驱动双曲柄四环板针摆行星传动进行可行性提出建议与优化措施研究方法：1. 理论分析法：通过理论计算和分析双驱动双曲柄四环板针摆行星传动的结构和性能参数2. 计算机仿真法：利用ADAMS软件建立双驱动双曲柄四环板针摆行星传动模型，进行运动学仿真分析3. 实验方法：制作实物样机，进行实验验证，对比理论计算与计算机仿真的结果预期成果：1. 探究双驱动双曲柄四环板针摆行星传动的设计原理及结构组成2. 分析可行性并进行性能参数计算3. 建立模型并进行仿真分析4. 进行实验研究，验证模型与仿真分析的结果5. 提出优化建议参考文献：1. Liu, J., Yin, Z., & Chen, H. (2020). A new self-balanced 2-DOF spatial spherical parallel manipulator with orthogonal co-axial rotational inputs. Mechanism and Machine Theory, 145, 103740.2. Dai, J. S. (2018). Positive Solutions of Overconstrained Spatial Compliant Mechanisms without Auxiliary Loops. Journal of Mechanisms and Robotics, 10(6), 061014.3. Tian, Y., Bai, S., Qi, W., Zhang, Y., & Wang, L. (2019). Geometric Analysis and Dynamic Evaluation of a Five-Degree-of-Freedom Suspended Cable-Driven Parallel Manipulator. Journal of Mechanisms and Robotics, 11(1), 011012.。

双曲柄环板式针摆行星传动的研究

双曲柄环板式针摆行星传动的研究以下将分步骤回答"[双曲柄环板式针摆行星传动的研究]" 这个主题。

一、什么是针摆行星传动？针摆行星传动是指由一个碟形齿轮作为太阳轮，固定在传动箱的输出轴上，通过数个针式行星轮和一个内齿环（或环板）构成的传动机构。

其中，针式行星轮由若干个针轮组成，针轮在行星架上摆动传递动力，实现传递和变速。

相比于其他传动方式，其具有高扭矩、高承载能力、高刚度、小体积和平滑运行等优点，广泛应用于工业、航空航天和机器人等领域。

二、双曲柄环板式针摆行星传动的构造双曲柄环板式针摆行星传动，在传统的针摆行星传动的基础上，加入了双曲柄和环板，以优化其传动性能。

其具体构造如下：太阳轮位于传动箱输出轴上面，通过轴承与输出轴连接；内齿环与输出轴固定在传动箱外壳上；行星架由若干个三角形构成，每个三角形有一个针轮和两个针摆点；行星架与内齿环相切，并通过架连杆与双曲柄相连，连杆的头尾分别与双曲线段相连；环板由若干片板组成，板间通过拉杆相连。

三、双曲柄环板式针摆行星传动的工作原理当太阳轮转动时，由于双曲柄的特点，行星架会沿着内齿环同时旋转和振动，使得行星轮沿针摆点振动，实现动力的传递和变速。

在行星轮振动过程中，环板通过拉杆向内齿环施加一个反向力，以避免振动幅度过大。

此时，双曲柄的作用是通过改变行星架振动中的架连杆长度，以实现不同的变速比。

具体来说：当太阳轮以一定速度转动时，双曲柄引导行星架流动，令行星轮形成大幅振动，实现大的变速比；当太阳轮转速变快时，针轮在转速上的限制导致针轮振动振幅缩小，从而实现小的变速比。

四、双曲柄环板式针摆行星传动的应用前景双曲柄环板式针摆行星传动具有高扭矩、高刚度和小体积等优点，已经在机器人、重载机械和制造装备等领域得到广泛应用。

在未来，随着科技的不断发展，这种传动方式的应用将会进一步扩展。

例如，在火星探索等领域，双曲柄环板式针摆行星传动可以作为调节机器人探测器方向和速度的核心装置，具有广阔的应用前景。

同步带双曲柄环板式针摆减速器[实用新型专利]

专利名称：同步带双曲柄环板式针摆减速器专利类型：实用新型专利
发明人：何卫东,余鹰,李欣,李力行,林绚丽申请号：CN96207312.1
申请日：19960401
公开号：CN2258239Y
公开日：
19970723
专利内容由知识产权出版社提供
摘要：本实用新型的减速器，是一种同步带联动双曲柄的环板式针摆减速器，包括输入轴、从动曲柄轴和输出轴；输入轴和从动曲柄轴上分别至少固定有一个偏心轴套；至少一个齿环板上的针齿与固定在输出轴上的摆线轮形成小齿差啮合传动；输入轴和从动曲柄轴上分别安装齿形带轮，并通过齿形带的凸齿与带轮齿槽啮合，实现无滑动传递运动和动力，能使双曲柄机构顺利通过死点。

本实用新型具有多齿啮合，重合度大大增加，承载能力大，传动平稳，体积小、重量轻，以及寿命长和传动效率高的特点。

申请人：何卫东,余鹰,李欣
地址：116028 辽宁省大连市大连铁道学院353号
国籍：CN
更多信息请下载全文后查看。

Harmonicdrive摆线行...

重庆大学硕士学位论文摆线包络行星传动接触强度及本体温度场研究姓名:谭磊申请学位级别:硕士专业:机械制造及其自动化指导教师:陈兵奎2010-05重庆大学硕士学位论文中文摘要摘要课题来源于国家科技支撑计划课题“摆线包络行星精密传动研究”编号:2006BAF01B08。

精密传动是以高精度传动运动为主要目的一类机械传动形式,在武器装备、数控机床、机器人、医疗器械、航空与航天、交通运输机械、印刷包装机械等领域应用十分广泛,是装备制造业和国防工业中极其重要的基础性零部件。

摆线包络行星传动具有多齿啮合、传动精度高、承载能力强、扭转刚度高等突出优点,近年来在机器人、航天航空领域有广泛的应用前景,受到了广泛关注。

本文将着重研究摆线一次及二次包络啮合副接触强度及本体温度场的计算分析方法,为啮合副的设计提供重要理论依据。

论文的主要内容包括:①根据齿轮啮合原理的运动学法,分别介绍了摆线一次及二次包络行星传动共轭啮合理论,并研究了摆线二次包络行星传动的啮合特性及曲率半径、综合曲率半径的计算方法。

②基于赫兹接触理论和摆线包络行星传动啮合理论,对摆线一次及二次包络啮合副的接触强度进行理论研究,推导出理论接触强度计算公式,为摆线包络行星传动接触强度计算及有限元分析提供了理论依据和参考。

③在简要介绍有限元法基础上,运用 ANSYS 及其 APDL 语言建立摆线一次及二次包络啮合副接触有限元分析模型,调用 ANSYS求解器进行求解,并对结果进行对比分析。

④根据齿轮啮合原理和传热学基本理论,研究了摆线一次及二次包络啮合副本体温场分析热边界条件及其计算方法,并运用 ANSYS 进行啮合副的本体温度场有限元仿真分析。

⑤综合运用 Visual Basic 6.0 和 APDL参数化有限元分析技术对 ANSYS进行二次开发,编制了摆线包络啮合副齿廓设计及有限元分析系统,实现了啮合副设计及分析的一体化、自动化和参数化。

关键词:摆线,接触强度,有限元分析,本体温度场,ANSYSI 重庆大学硕士学位论文英文摘要ABSTRACTThe project originates from the National Science and Technology SupportingProgram, named “The R esearch on Cycloid Enveloping Planetary PrecisionTransmission” No. 2006BAF01B08. Precision transmission is a kind of mechanicaltransmission mainly focuses on high-precision transmission of movement, it is widelyweapon equipments,used in many fields, such as aviation and spaceflight, robot, NCmachine tools, medical apparatus, transportation machinery printing, packagingmachinery and so on. Precision transmission is an extremelyimportant basic componentdefense industry and the equipment manufacturing industryinCycloid enveloping planetary transmission has advantages of multi-tooth meshing,high-precision of transmission; strong bearing capacity and high torsional stiffness. So it has beenpaid a wide rage of attention in the filed of precise transmission. This paper primarily studies contact strength and bulk temperature of the single and secondary enveloping cycloid meshing pair, whichcan provide a theoretical basis for the design of meshing pair, and has the practical engineeringsignificance. The main contents of this thesis as follows:①According to principle of gears meshing kinematics method, conjugate theorysingle and secondary enveloping cycloid meshing pair has been introduced, and the meshingof thefeatures, radius of curvature and comprehensive radius of curvature of the secondary envelopingcycloid enveloping planetary transmission have been discussed②Based on Hertz, theoretical contact theory and the theory of cycloid envelopingplanetary transmission, the contact strength of single and secondary enveloping cycloidmeshing pair has been studied. Contact strength formulas have been derived, which can provide atheoretical basis and reference for the contact strength calculation and finite element analysis forcycloid enveloping planetary transmission③Based on brief introduction of finite element method, the finite element modelsof secondary enveloping cycloid meshing pair and single-enveloping cycloid meshingpair are built and analyzed by ANSYS and APDL, and results are analyzed andcompared④ According to gear meshing theory and the basic theory of hear transfer, thecalculating method of thermal boundary conditions of body temperature filed analysis single and secondary enveloping cycloid meshing pairof are carried out. The body temperaturefiled of meshing pair is analyzed by ANSYSII 重庆大学硕士学位论文英文摘要⑤ Visual Basic 6.0 and APDL, which is a second development tool provided byANSYS, are used to develop the program of tooth profile design and finite elementanalysis in cycloid enveloping planetary transmission. by using it, the integration,automation and parameterization of design and analysis of meshing pair is achievedKeywords: Cycloid enveloping planetary transmission, contact strength, finite elementanalysis, bulk temperature, ANSYSIII 重庆大学硕士学位论文 1 绪论1 绪论1.1 课题来源以及研究的意义课题来源于国家科技支撑计划“摆线包络行星精密传动研究”(课题编号:2006BAF01B08)精密传动是以高精度传动运动为主要目的一类机械传动形式,在航空与航天、数控机床武器装备、土建机械、机器人、印刷包装机械、医疗器械、交通运输机械等领域应用十分广泛,是制造装备业和国防工业中极其重要的基础性零部件。

机械原理术语英汉对照

机械原理重要名词术语中英文对照表Aarchimedes worm 阿基米德蜗杆BFifth-power polynomial motion 五次多项式运动规律oscillating follower 摆动从动件cam with oscillating follower 摆动从动件运动规律oscillating guide-bar mechanism 摆动导杆机构cycloidal gear 摆线齿轮cycloidal motion 摆线运动规律cycloidal-pin wheel 摆线针轮angle of contact 包角back cone 背锥back angle 背锥角back cone distance 背锥距scale 比例尺closed kinematic chain 闭式运动链closed chain mechanism 闭式链机构arm 臂部modified gear 变位齿轮modification coefficient 变位系数standard spur gear 标准直齿轮combine in parallel 并联式组合amount of unbalance 不平衡量intermittent gearing不完全齿轮wave generator 波发生器number of waves 波数Cgeneva wheel 槽轮geneva mechanism 槽轮机构groove cam 槽凸轮backlash 侧系differential gear train 差动轮系differential screw mechanism 差动螺旋机构differentials 差速器space 齿槽space width 齿槽宽addendum 齿顶高addendum circle 齿顶圆dedendum 齿根高dedendum circle 齿根圆thickness 齿厚circular pitch 齿距face width 齿宽tooth profile 齿廓tooth curve 齿廓曲线gear 齿轮pinion and rack 齿轮齿条机构pinion cutter 齿轮插刀hob,hobbing cutter 齿轮滚刀gears 齿轮机构blank 齿轮轮坯teeth number 齿数gear ratio 齿数比rack 齿条rack cutter 齿条插刀coincident points 重合点contact ratio 重合度transmission ratio, speed ratio 传动比transmission angle 传动角combine in series 串连式组合driven pulley 从动带轮driven link, follower 从动件width of flat-face 从动件平底宽度follower dwell 从动件停歇follower motion 从动件运动规律driven gear 从动轮Dbelt drives 带传动belt pulley 带轮universal joint 单万向联轴节unit vector 单位矢量equivalent spur gear 当量齿轮equivalent teeth number 当量齿数equivalent coefficient of friction 当量摩擦系数cutter 刀具lead 导程lead angle 导程角constant acceleration and deceleration motion 等加速等减速运动规律constant diameter cam等径凸轮constant breadth cam 等宽凸轮uniform motion, constant velocity motion等速运动规律equivalent link 等效构件equivalent force 等效力equivalent moment 等效力矩equivalent mass 等效质量equivalent moment of inertia 等效惯性力lower pair 低副clearance 顶隙ordinary gear train 定轴轮系dynamic balance 动平衡dynamic balancing machine 动平衡机dynamic characteristics 动态特性dynamic reaction 动压力dynamic load 动载荷transverse plane 端面transverse parameters 端面参数transverse circular pitch 端面齿距transverse contact ratio 端面重合度transverse module 端面模数transverse pressure angle 端面压力角inline roller follower对心滚子从动件inline flat-faced follower 对心平底从动件inline slider crank mechanism对心曲柄滑块机构in-line translating follower对心移动从动件polynomial motion 多项式运动规律rotor with several masses 多质量转子idler gear 惰轮Fgenerating line 发生线generating plane 发生面normal plane法面normal paramenters 法面参数normal circular pitch 法面齿距normal module 法面模数normal pressure angle 法面压力角feedback combining 反馈式组合inverse cam mechanism 反凸轮机构inverse (backward) kinematics 反向运动学kinematic inversion 反转法generating 范成法form cutting 仿形法flywheel飞轮moment of flywheel 飞轮距nonstandard gear非标准齿轮aperiodic speed fluctuation 非周期性速度波动noncircular gear非圆齿轮standard pitch line分度线standard pitch circle分度圆standard pitch cone分度圆锥planetary differential封闭差动轮系additional mechanism附加机构compound hinge 复合铰链compound combining复合式组合compound screw mechanism复式螺旋机构complex mechanism复杂机构Ginterference干涉rigid circular spline刚轮body guidance mechanism 刚体导引机构rigid impulse (shock) 刚性冲击rigid rotor 刚性转子higher pair高副grashoff’s law 格拉晓夫定理undercutting根切working space工作空间effective resistance工作阻力effective resistance moment工作阻力矩working stroke 工作行程common normal line 公法线general constraint公共约束metric gears公制齿轮power 功率conjugate profiles共轭齿廓conjugate cam共轭凸轮link 构件fixed link, frame 固定构件jointed manipulator关节型操作器inertia force惯性力partial balance of shaking force 惯性力部分平衡moment of inertia, shaking moment惯性力矩balance of shaking force 惯性力平衡full balance of shaking force 惯性力完全平衡path generator轨迹发生器hob，hobbing cutter滚刀roller滚子radius of roller 滚子半径roller follower 滚子从动件undercutting 过度切割Hfunction generator函数发生器interchangeable gears互换性齿轮slider 滑块return，return-stroke 回程compound gear train 复合轮系Jmechanism 机构analysis of mechanism机构分析balance of balance机构平衡mechanism机构学kinematic design of mechanism机构运动设计kinematic diagram 机构运动简图synthesis of mechanism机构综合constitution of mechanism机构组成frame，fixed link机架kinematic inversion 机架变换machine机器robot 机器人manipulator 机器人操作器robotics 机器人学machinery 机械dynamic analysis of machinery机械动力分析dynamic design of machinery 机械动力设计dynamics of machinery 机械动力学mechanical advantage机械利益balance of machinery 机械平衡manipulator机械手mechanical behavior 机械特性mechanical efficiency机械效率mechanisms and machine theory, theory of mechanisms and machines机械原理coefficient of speed fluctuation机械运转不均匀系数fundamental mechanism 基础机构base circle基圆radius of base circle 基圆半径base pitch 基圆齿距pressure angle of base circle 基圆压力角base cylinder 基圆柱base cone 基圆锥quick-return mechanism 急回机构quick-return characteristics 急回特性quick-return motion 急回运动ratchet棘轮ratchet mechanism棘轮机构pawl 棘爪extreme position极限位置crank angle between extreme positions 极位夹角computer aided design计算机辅助设计computer integrated manufacturing system 计算机集成制造系统acceleration加速度acceleration analysis加速度分析acceleration diagram 加速度曲线knife-edge follower尖底从动件intermittent motion mechanism 间歇运动机构simple harmonic motion (SHM for short) 简谐运动involute helicoid 渐开线螺旋面involute 渐开线involute profile 渐开线齿廓involute gear 渐开线齿轮generating line of involute 渐开线发生线involute equation 渐开线方程involute function 渐开线函数involute worm 渐开线蜗杆pressure angle of involute 渐开线压力角simple harmonic motion 简谐运动cross-belt drive交叉带传动crossed helical gears交错轴斜齿轮angular acceleration 角加速度angular velocity 角速度angular velocity ratio 角速比correcting plane校正平面structure 结构structural and mechanical error 结构误差pitch point 节点pitch line节线pitch circle 节园thickness on pitch circle 节园齿厚pitch diameter节圆直径pitch cone 节圆锥pitch cone angle节圆锥角analytical design 解析设计diametral pitch 径节clearance 径向间歇static balance 静平衡passive degree of freedom 局部自由度absolute motion 绝对运动absolute velocity 绝对速度load balancing mechanism 均衡装置Kopen-belt drive 开口传动open kinematic chain 开式链open chain mechanism 开式链机构spatial mechanism 空间机构spatial linkages 空间连杆机构spatial cams 空间凸轮机构spatial kinematic pair 空间运动副spatial kinematic chain 空间运动链block diagram 框图Lpitch curve 理论廓线force 力force polygon 力多边形force-closed cam mechanism 力封闭型凸轮机构moment 力矩equilibrium 力平衡couple [of forces], couples 力偶moment of couple 力偶矩connecting rod, couple 连杆linkages 连杆机构couple curve 连杆曲线line of centers 连心线chain wheel 链轮two-dimensional cam 两维凸轮critical speed 临界转速six-bar linkage 六杆机构blank 轮坯gear train 轮系screw 螺杆thread pitch 螺矩nut, screw nut螺母thread of a screw 螺纹helical pair 螺旋副screw mechanism 螺旋机构helical angle 螺旋角helix, helical line 螺旋线Mmodule 模数friction摩擦friction angle 摩擦角friction force 摩擦力friction moment 摩擦力矩coefficient of friction 摩擦系数friction circle 摩擦圆end-effector 末端执行器objective function 目标函数Nmechanism with flexible elements 挠性机构flexible rotor 挠性转子internal gear 内齿轮ring gear 内齿圈engaging-out啮出engagement, meshing engagement, meshing 啮合meshing point 啮合点angle of engagement 啮合角contacting line, pressure line, line of engagement 啮合线length of contacting line 啮合线长度engaging-in啮入nomogram诺模图Pdisk cam 盘形凸轮parabolic motion抛物线运动belt pulley 皮带轮offset distance 偏距offset circle 偏距圆eccentric 偏心盘offset roller follower 偏置滚子从动件offfser knife-edge follower 偏置尖底从动件offset flat-face follower 偏置平底从动件offset slider-crank mechanism 偏置曲柄滑块机构frequency频率flat belt drive 带传动flat-face follower 平底从动件face width 平底宽度balance 平衡balancing machine 平衡机balancing quality 平衡品质correcting plane 平衡平面balance mass, quality of mass 平衡质量counterweight 平衡重balancing speed 平衡转速planar pair, flat pair 平面副planar mechanism 平面机构planar kinematic pair 平面运动副planar linkage 平面连杆机构planar cam 平面凸轮parallel helical gears 平行轴斜齿轮Qother mechanism most in use 其它常用机构starting period 起动阶段pneumatic mechanism 气动机构singular position 奇异位置initial contact ,beginning of contact 起始啮合点forced vibration 强迫振动depth of cut 切齿深度crank 曲柄grashoff’s law曲柄存在条件rotation guide-bar mechanism 转动导杆机构slider-crank mechanism 曲柄滑块机构crank-rocker mechanism曲柄摇杆机构curvature曲率radius of curvature 曲率半径curved-shoe follower曲面从动件curve matching 曲线拼接driving force驱动力driving moment 驱动力矩whole depth全齿高spherical pair球面副spherical involute 球面渐开线spherical motion球面运动sphere-pin pair球销副polar coordinate manipulator球坐标操作器Rherringbone gear，double helical gear 人字齿轮redundant degree of freedom 冗余自由度flexspline 柔轮flexible impulse, soft shock 柔性冲击flexible manufacturing system 柔性制造系统flexible automation 柔性自动化Sthree-dimensional cam 三维凸轮kennedy’s theorem，theorem of three centers 三心定理planetary drive with small teeth difference 少齿差行星传动design variable 设计变量rise 升程cam profile 实际廓线real part 实部vector矢量output work输出功output link 输出构件output mechanism 输出机构output torque 输出力矩output shaft 输出轴input link 输入构件mathematical model 数学模型double-slider mechanism, ellipsograph 双滑块机构double crank mechanism 双曲柄机构constant-velocity universal joints 双万向联轴节double rocker mechanism 双摇杆机构oldham coupling 双转块机构instantaneous center 瞬心dead point 死点four-bar linkage 四杆机构velocity 速度speed fluctuation 速度波动coefficient of speed fluctuation 速度波动系数velocity diagram 速度曲线instantaneous center of velocity 速度瞬心Tstep pulley 塔轮sun gear 太阳轮characteristics 特性equivalent mechanism 替代机构governor调速器stopping phase 停车阶段dwell 停歇synchronous belt drive同步带传动cam 凸轮cams, cam mechanism 凸轮机构cam profile 凸轮(实际)廓线layout of cam profile 凸轮廓线绘制pitch curve 凸轮理论廓线graphical design 图解设计rise 推程Wexternal gear 外齿轮external force 外力universal joint, hooke’s coupling 万向联轴节wrist 腕部reciprocating motion 往复移动differential screw mechanism 差动螺旋机构displacement 位移displacement diagram 位移曲线pose, position and orientation 位姿steady motion period 稳定运转阶段robust design 稳健设计worm 蜗杆worm gearing 蜗杆传动机构number of threads 蜗杆头数diametral quotient 蜗杆直径系数worm and worm gear 蜗杆蜗轮机构worm gear 蜗轮Xcrank arm, planet carrier 系杆field balancing 现场平衡centrifugal force 离心力relative velocity 相对速度relative motion 相对运动pinion 小齿轮harmonic drive 谐波传动helical gear 斜齿圆柱齿轮stroke 工作行程coefficient of travel speed variation, advance-to return-time ratio 行程速比系数planet gear 行星轮planet gear train行星轮系planet carrier 行星架form-closed cam mechanism 形封闭凸轮机构virtual reality 虚拟现实redundant constraint 虚约束imaginary part 虚部allowable amount of unbalance 许用不平衡量allowable pressure angle 许用压力角circulating power load 循环功率流Ypressure angle 压力角jacobi matrix 雅克比矩阵rocker 摇杆hydrodynamic drive 液力传动hydraulic mechanism 液压机构reciprocating follower 移动从动件sliding pair, prismatic pair移动副prismatic joint 移动关节wedge cam 移动凸轮increment or decrement work 盈亏功optimal design 优化设计detrimental resistance有害阻力simple harmonic motion 余弦加速度运动round belt drive 圆带传动circular gear 圆形齿轮cylindric pair 圆柱副cylindrical cam 圆柱凸轮cylindrical worm 圆柱蜗杆cylindrical coordinate manipulator 圆柱坐标操作器bevel gears 圆锥齿轮机构cone angle 圆锥角driving link 原动件constraint 约束constraint condition 约束条件jerk 跃度jerk diagram 跃度曲线kinematic inversion 运动倒置kinematic analysis 运动分析kinematic pair 运动副moving link 运动构件kinematic diagram 运动简图kinematic chain 运动链motion skewness 运动失真kinematic design 运动设计cycle of motion 运动周期kinematic synthesis 运动综合coefficient of velocity fluctuation 运动不均匀系数Zload 载荷generating 展成法，范成法tension pulley 张紧轮vibration 振动shaking couple 振动力矩frequency of vibration 振动频率amplitude of vibration 振幅tangent mechanism正切机构direct (forward ) kinematics 正向运动学sine generator, scotch yoke 正弦机构spur gear 直齿圆柱齿轮cartesian coordinate manipulator 直角坐标操作器diametral quotient 直径系数mass-radius product 质径积mid-plane 中间平面center distance 中心距center distance change 中心距变动central gear 中心轮final contact，end of contact 终止啮合点periodic speed fluctuation 周期性速度波动epicyclic gear train 周转轮系toggle mechanism 肘形机构shaft angle 轴角axial thrust load 轴向分力driving gear 主动齿轮driving pulley主动带轮rotating guide-bar mechanism 转动导杆机构revolute pair 转动副revolute joint 转动关节rotor 转子balance of rotor 转子平衡assembly condition 装配条件bevel gear 锥齿轮common apex of cone 锥顶cone distance 锥距cone pulley 锥轮sub-mechanism 子机构automation 自动化self-locking 自锁degree of freedom (dof for short )自由度total contact ratio 总重合度resultant force 总反力overlap contact ratio 纵向重合度combined mechanism 组合机构minimum teeth number 最少齿数minimum radius 最小向径applied force 作用力coordinate frame 坐标系。

外文文献翻译一个串行模式双驱动器单元行

一个串行模式双驱动器单元行星齿轮火车:基本设计和应用Byeong-sang kim，jae-bok song，member，IEEE，andjung-jun park 【摘要】：一个机器人机械臂的控制接触环境通常是由直接反馈控制系统的传感器或使用力偶间接阻抗控制方案。

虽然这些方法已成功地应用于许多应用程序，但与此同时控制力和位置却不能实现。

为应对这些问题，本文提出了一种新的设计的双驱动器单元(挣扎)两部分组成一个行星齿轮传动系统的执行器和提供之能力，同时控制中的地位和刚度。

既然一个致动器的控制地位和其他致动器调转刚度，挣扎着，可以控制的位置和刚度同时在同一关节。

两个施加的扭矩在关节与刚度的环境可以估计没有一个昂贵的力传感器。

实验表明，该挣扎着各种各样能钻头提供性能好、位置跟踪、力估算和环境评价。

力量指数环境条款估计，，行星轮系，冗余并联阻抗方法、变量(通过)。

【关键词】：机器人，行星齿轮，传感器.第一章简介机械手的运行是在自由空间能够控制的常规位置控制方案。

在这种情况下，通常具有高刚度机械手为提高定位精度。

当机械臂与外部环境接触或碰撞，这样的高刚度对双方都可能造成损害的机械手，保护我们的环境。

因此，在这种情况下，准确的力控制必须确保安全、平稳运动。

人们做了大量的研究性能提高的位置和力控制[1]-[12]。

例如，力控制执行一个操作臂，通常是直接由反馈控制系统，利用力传感器。

该方法需要复杂的算法，用一种昂贵的传感器。

此外，直接力控制可以使系统不稳定的当接触发生。

另一方面，力控制可以实现控制方法间接通过刚度的接触力是间接控制的调整期望位置的机器人末端执行器。

这个问题与间接力控制策略是，除非力量无法准确的环境管制模型以[13]。

来应付这个问题，那么这个变量的阻抗方法(通过)已被引入了一个好方法，可以同时控制刚度和位置的机器人手臂。

这个方法可以实现变刚度可以分为三种方法。

第一种方法利用受体激动剂/拮抗剂方法的激励的骨骼肌肉系统[14]、[15]。

多行星排变速箱传动效率分析与计算——陈永强

毕业论文（设计）题目多行星排变速箱传动效率分析与计算系部机械工程系专业机械设计制造及其自动化年级 2008级学生姓名陈永强学号 080664010 指导教师牟柳晨（老师）多行星排变速箱传动效率分析与计算四川大学锦江学院机械工程系学生：陈永强指导老师：牟柳晨【摘要】行星式动力换档变速箱具有：可采用小模数齿轮，零件受力平衡稳定，尺寸小，结构紧凑，结构刚度大，使用寿命长，操纵系统可靠性高，控制方便，传动形式效率较高等优点。

主要应用于轮胎式装载机、推土机、铲运机、平地机等，其技术也比较成熟。

效率是一个机器最重要的参数之一，本文探讨多行星排变速箱的传动效率，对于以后帮助选择、设计和改进行星传动进而提高效率都有着重要的意义。

本文略去液力损失(润滑油的搅动和飞溅损失)，只考虑齿轮的啮合摩擦损失和轴承的摩擦损失，运用基本方法——速比法对D6D变速箱进行效率计算与分析,并用基于VC++6.0、Delphi、VB6.0的行星变速箱分析系统进行计算机辅助分析。

【关键词】行星齿轮变速箱传动效率计算分析Analysis and calculation of the multi-planetary line gearboxtransmission efficiency【Abstract】Planetary power shift transmission has: can be small module gear, parts by the force balance and stability, small size, compact structure, structural rigidity, long life, high reliability control system, easy to control, higher efficiency of transmission form advantages. Are mainly used wheel loaders, bulldozers, scrapers, motor graders, and their technology is more mature. Efficiency is one of the most important parameters of a machine, this paper investigates the transmission efficiency of the transmission of multi-planetary line of great significance for later assist in the selection, design and improvement of the planetary transmission and thus improve the efficiency. This article omitted the hydraulic losses (oil and stir and splash loss), and consider only the gear meshing friction loss and the friction losses in the bearings, the use of the basic method - speed ratio method for the D6D transmission efficiency calculation and analysis, and based on VC + + 6.0, Delphi, VB6.0 planetary gearbox analysis system for computer-aided analysis.【Keyword】Planet Transmission Transmission efficiency Calculate Analysis目录绪论 (1)1 变速箱的发展、现状、趋势 (1)1.1 我国变速箱的发展概况 (1)1.2 变速箱的现状 (2)1.2.1国外变速箱的发展现状 (2)1.2.2国内变速箱的发展现状 (3)1.3变速箱的趋势 (3)1.3.1国外变速箱的发展趋势 (3)1.3.2国内变速箱的发展趋势 (4)2 变速箱 (4)2.1 变速箱的功用、原理、要求 (4)2.1.1 变速箱的功用[5] (4)2.1.2变速箱的原理 (4)2.1.3 对变速箱的要求[6] (5)2.2 变速箱的类型 (5)2.2.1 按使用方法分 (5)2.2.2 按传动比变化分 (5)2.2.3 按换挡方式分 (5)2.2.4 按轮系型式分 (6)2.3 变速箱的比较 (6)2.3.1 人力换挡与动力换挡 (6)2.3.1.1人力换挡变速箱 (6)2.3.1.2动力换挡变速箱 (6)2.3.2 定轴式与行星式 (7)2.3.2.1定轴式动力换挡变速箱 (7)2.3.2.2行星式动力换挡变速箱 (7)3 行星排分析[8] (7)3.1 行星排的运动分析 (8)3.2 行星排的动力学分析 (9)3.3 行星排的功率分析 (10)3.4 行星排的效率计算 (10)3.4.1 啮合功率法 (10)3.4.2 力矩法求效率 (11)3.4.3 速比法求效率[10] (11)4 行星变速箱的传动分析和功率流分析 (12)4.1 行星变速箱的组成 (12)4.2 自由度分析 (12)4.3 档位数分析 (12)4.4 行星变速箱转速分析 (13)4.5 各构件的转矩分析 (13)4.6 行星传动的功率流分析 (14)4.6.1 功率流的传递 (14)4.6.2 循环功率 (14)5 多行星排变速箱效率分析与计算 (15)5.1 速比法[10] (15)5.2 D6D结构特征[12] (17)5.3 D6D变速箱档位分析 (17)5.4 传动比计算 (17)5.5 传动效率计算 (21)5.6 效率分析 (25)6 行星变速箱计算机辅助分析[14] (26)6.1 基于VC++6.0的行星变速箱分析系统 (26)6.1.1 VC++6.0简介[15] (26)6.1.2 系统程序简介 (26)6.2 基于Delphi的行星变速箱设计系统[10] (27)6.2.1 Delphi简介[16] (27)6.2.2 设计系统简介 (27)6.3 基于VB6.0的行星变速箱分析系统 (28)总结及展望 (29)参考文献 (30)致谢 (31)绪论随着现代工业的飞速发展，对齿轮传动的效率、可靠性、体积、重量、承载能力等经济技术指标越来越高，行星齿轮传动就是重要的齿轮传动形式之一，讨论分析其传动效率对动力换挡行星变速箱有着重要的意义。

双电机驱动双曲柄四环板式针摆行星传动研究

1
以 l = rp - rc 代入式 ( 1) 得,
图 1 双曲柄环板式针摆行星传动机构简图
图 2 双电机驱动双曲柄四环板针摆行星传动机构简图
由图 1 可以看出 , 摆线轮和针轮在啮合处 P 点的速度方向要与 vB 相同 , 则摆线轮 5 绕 O c 的转动方向必与主动曲柄绕 A 的转动方向相反. 即若 1 的转向为逆时针, 则环板式针摆行星传动的传动比计算公式应写为 i15 =
摆线针轮行星传动具有体积小、重量轻、传动比范围大、传动效率高、传动平稳且可靠等一系列优点 , 但它也有一薄弱环节, 即转臂轴承处于摆线轮上输出机构的内部, 径向尺寸受到限制, 从而限制了摆线针轮行星传动更充分地发挥其承载能力 . 为大幅度提高机械传动装置的承载能力、传动效率和可靠性诸指标 , 作者创新研究出来的多种结构双曲柄环板式针摆行星传动 ( 已获国家专利 , 专利号: ZL 02231994 . 8) 其特点是不仅保留着原摆线针轮行星减速器同时啮合齿数多、总法向力与总圆周力间夹角小、摆线轮与针轮齿均为硬齿面等本质上的优点, 而且用双曲柄作为主动杆 , 让装于连杆上的针轮拨动摆线轮 , 可让转臂轴承由行星轮内移至行星轮外, 尺寸不再受限制 , 从而传递的转矩可以较现有的摆线针轮行星减速器成倍增大 , 除此之外 , 省去输出机构后会使输出轴刚性更好 . 本项目对这一创新传动的优化设计理论与制造技术进行了深入研究 , 成功地研制出了 3 种型式的样机 , 并在实验室进行了样机台架性能试验 , 试验结果充分地证明了这种创新传动的优越性. 因此 , 双曲柄环板式针摆行星传动的研制成功, 必将为国民经济各工业部门提供一种体积小、传动比范围大、传动效率高、传动平稳、输出轴刚度大、传递的转矩和功率可以更大的极有实用价值的新型摆线针轮行星传动.

曲柄压力机的改良外文翻译

陕西理工学院毕业设计英文资料翻译2012年6月1日UNITED STATES PATENT OFFICECHARLES H. LASKER, OF JOLIET, ILLINOISOPERATING MEANS FOR A CRANK PRESSApplication filed May 5, 1932. Serial No. 609,365The subject of my invention is an operating means for a crank press, such as a brick press.It is the object of my invention to provide means whereby a press of the crank or rotary type, which has reciprocating parts driven by a rotating engine, is enabled to move at slow speed during the working cycle and at high speed during the opening and closing cycle when the press may be run at slow speeds when working and thus give a pressure comparable to that of an hydraulic press and yet move with such speed during the non-working cycle as to give the high production required of modern machinery.An embodiment of my invention consists in a crank press, a motor for said press , means for driving said press from said motor at high speed, means for driving said press from said motor at slow speed, and means for selecting one or other of said previously mentioned means in accordance with the position of the press.For a further exposition of my invention reference may be had to the annexed drawing and specification at the end where of my invention will be specifically pointed out and claimed.Figure 1 represent an elevation of my device with parts in cross section and in diagram.Figure 2 is a diagrammatic view of a portion of my device.In that embodiment of my invention chosen for illustration in the drawing my device is shown as consisting of a motor of any convenient type, such as an electric motor. Motor 1 has shaft 2 connected thereto which carries fly-wheel 3 and gear 4. Gear 4 meshes with gear 5 on a lay-shaft or counter-shaft 6 which also carries a gear 7 thereon. Gear 7 meshes with gear 8 which is mounted for rotation on the sleeve of the driving member 10 of the clutch generally indicated at L. Clutch L also includes a driven member 11. Mounted on shaft 2 is driving member 100 of clutch H which also includes driven member 111 fast on stub shaft 12 which also carries driven member 11. Shaft 12 carries gear 13 which meshes with a train of gears to drive crank shaft 14 of the press generally indicated at 15. Crank shaft 14 carries at one end a gear 16 which has a pin 17 mounted thereon. Gear 16 meshes with another gear 18 which carries a pin 19 thereon. Switch 20 is pivotally mounted at 21 adjacent gears 16 and 18 so that the arms 22 and 23 cooperate with the pins 17 and 19 respectively to move switch 20 so that the contacts indicated at 24 and 25 are respectively operated. Wires 26 and 27 connect contacts 24 25 with clutches H and L respectively so that as switch 20 is moved from one position to the other either clutch H or clutch L is actuated to connect or to disengage its driving and driven members. Wires 28 are a source of current for switch 20 and for clutches H and L.As shown in Figure 3 it is the purpose of my invention to move the press 15 at low speed from the point A to the point B on the diagram in Figure 3, this being the working cycle of the press. The press 15 is moved at high speed during thecycle represented from point B to point A of Figure 3, this being the non-working cycle of the press.In the operation of my device motor 1 is started and drives press 15 either at high or low speed depending upon whether clutch H or clutch L is in engagement. During the pressing cycle the driving is from motor 1, shaft 2, gears 4 and 5, lay shaft 6, gears 7 and 8, clutch L, stub shaft 12, gear 13 to crank shaft 14. When the pressing cycle of the press is complete switch 20 is shifted by means of pin 17 so that clutch L is disengaged and clutch H is engaged. Motor 1 then drives press 15 though the following connections, shaft 2, clutch H, stub shaft 12, gear 13 and crank shaft 14.I do not intend to be limited in the practice of my invention save as the scope of the prior art and of the attached claims may require.I claim:1. operating means for a power press including in combination a motor, a power press driven by said motor, means for driving said press from said motor at high speed, means for driving said press from said motor at slow speed, and means for selecting one or other of said last mentioned means according to the position of said press.2. Operating means for a crank press including in combination a motor, a crank press adapted to be driven by said press from said motor at high speed, a second train of gearing for driving said press from said motor at slow speed, and means dependent upon the position of said press for selecting first or saidsecond train of gearing.3. Operating means for a crank press including in combination a motor, a crank press adapted to be driven by said motor, a train of gearing for driving said press from said motor at high speed, a second train of gearing for driving said press from said motor at low speed, a plurality of clutches controlling said train of gearing, and means for connecting one and disengaging the other of said clutches depending upon the position of said press.4. Operating means for a crank press including in combination a motor, a crank press adapted to be driving by said motor, a train of gearing for driving said press from said motor at high speed, a clutch controlling said train of gearing , a second train of gearing for driving said press from said motor at low speed , a second clutch controlling said second train of gearing, and means including an electric switch for connecting one and disengaging the other of said clutches depending upon the position of said press.5. Operating means for a crank press including in combination a motor, a crank press adapted to be driven by said motor ,a train of gearing for driving said press from said motor at high speed, an electromagnetic clutch controlling said train of gearing, a second train of gearing for driving said press from said motor at slow speed, a second electromagnetic clutch controlling said second train of gearing, an electric switch actuated by said press for connecting one and disengaging the other of said clutches depending upon the position of said press, and a source of electricity for said switch and said clutches.6. Operating means for a crank press for manufacturing bricks including in combination a motor , a brick press of the crank type adapted to be driven by said motor, a motor shaft , a clutch driving member on said shaft, a lay-shaft, a gear on said motor shaft, a second gear on said lay-shaft, a stub shaft, a clutch driven member cooperating with said clutch driving member mounted on said stub shaft, a second clutch driven member mounted on said stub shaft, a second clutch driving member loosely mounted on said stub shaft, a gear for driving said second clutch driving member and meshing with said second gear on said lay-shaft, a crank shaft for said press, a train of gearing connecting said crank shaft to said stub shaft, a limit switch, means for actuating said limit switch from said crank shaft depending upon the position of said press, electrical connections between said clutch members and said limit switch where-by in either position of said limit switch one of said clutches is engaged and the other is disengaged, and a source of electricity for said limit switch and for said clutch.CHARLES H. LASKER.美国专利局查尔斯·H·拉斯克，伊利诺伊州乔利埃特，曲柄压力机的操作装置申请提出，1932年5月5日。

二级齿轮减速器外文翻译

Thegear and shaftReducer is a dynamic communication agencies, the use of gear speed converters, motor rotational speed reducer to the Rotary to be few, and have greater torque institutions. General helical gear reducer has reducer (including parallel shaft helical gear reducer, a worm reducer, bevel gear reducer, etc.), planetary gear reducer, Cycloid reducer, a worm reducer, a planetary friction CVT mechanical machines.The important position of the wheel gear and shaft can't falter in the design of he passing to process to make them can is divided into many model numbers , using for many situations respectively .So we must be the multilayer to the understanding of the wheel gear and shaft in reducer.In the force analysis of spur gears, the forces are assumed to act in a single plane. We shall study gears in which the forces have three dimensions. The reason for this, in the case of helical gears, is that the teeth are not parallel to the axis of rotation. And in the case of bevel gears, the rotational axes are not parallel to each other. There are also other reasons, as we shall learn.Helical gears are used to transmit motion between parallel shafts. The helix angle is the same on each gear, but one gear must have a right-hand helix and the other a left-hand helix. The shape of the tooth is an involutes helicoids. If a piece of paper cut in the shape of a parallelogram is wrapped around a cylinder, the angular edge of the paper becomes a helix. If we unwind this paper, each point on the angular edge generates an involutes curve. The surface obtained when every point on the edge generates an involutes is called an involutes helicoids.The initial contact of spur-gear teeth is a line extending all the way across the face of the tooth. The initial contact of helical gear teeth is a point, which changes into a line as the teeth come into more engagement. In spur gears the line of contact is parallel to the axis of the rotation; in helical gears, the line is diagonal across the face of the tooth. It is this gradual of the teeth and the smooth transfer of load from one tooth to another, which give helical gears the ability to transmit heavy loads at high speeds. Helical gearssubject the shaft bearings to both radial and thrust loads. When the thrust loads become high or are objectionable for other reasons, it may be desirable to use double helical gears. A double helical gear (herringbone) is equivalent to two helical gears of opposite hand, mounted side by side on the same shaft. They develop opposite thrust reactions and thus cancel out the thrust load. When two or more single helical gears are mounted on the same shaft, the hand of the gears should be selected so as to produce the minimum thrust load.Crossed-helical, or spiral, gears are those in which the shaft centerlines are neither parallel nor intersecting. The teeth of crossed-helical fears have point contact with each other, which changes to line contact as the gears wear in. For this reason they will carry out very small loads and are mainly for instrumental applications, and are definitely not recommended for use in the transmission of power. There is on difference between a crossed helical. Gear and helical gear until they are mounted in mesh with each other. They are manufactured in the same way. A pair of meshed crossed helical gears usually have the same hand; that is a right-hand driver goes with a right-hand driven. In the design of crossed-helical gears, the minimum sliding velocity is obtained when the helix angle are equal. However, when the helix angle are not equal, the gear with the helix angle should be used as the driver if both gears have the same hand.Worm gears are similar to crossed helical gears. The pinion or worm has a small number of teeth, usually one to four, and since they completely wrap around the pitch cylinder they are called threads. Its mating gear is called a worm gear, which is not a true helical gear. A worm and worm gear are used to provide a high angular-velocity reduction between nonintersecting shafts which are usually at right angle. The worm gear is not a helical gear because its face is made concave to fit the curvature of the worm in order to provide line contact instead of point contact. However, a disadvantage of worm gearing is the high sliding velocities across the teeth, the same as with crossed helical gears.Worm gearing are either single or double enveloping. A single-enveloping gearing is one in which the gear wraps around or partially encloses the worm.A gearing in which each element partially encloses the other is, of course, a double-enveloping worm gearing. The important difference between the two is that area contact exists between the teeth of double-enveloping gears while only line contact between those of single-enveloping gears. The worm and worm gear of aset have the same hand of helix as for crossed helical gears, but the helix angles are usually quite different. The helix angle on the worm is generally quite large, and that on the gear very small. Because of this, it is usual to specify the lead angle on the worm, which is the complement of the worm helix angle, and the helix angle on the gear; the two angles are equal for a 90-deg. Shaft angle.When gears are to be used to transmit motion between intersecting shaft, some of bevel gear is required. Although bevel gear are usually made for a shaft angle of 90 deg. They may be produced for almost any shaft angle. The teeth may be cast, milled, or generated. Only the generated teeth may be classed as accurate. In a typical bevel gear mounting, one of the gear is often mounted outboard of the bearing. This means that shaft deflection can be more pronounced and have a greater effect on the contact of teeth. Another difficulty, which occurs in predicting the stress in bevel-gear teeth, is the fact the teeth are tapered.Straight bevel gears are easy to design and simple to manufacture and give very good results in service if they are mounted accurately and positively. As in the case of spur gears, however, they become noisy at higher values of the pitch-line velocity. In these cases it is often good design practice to go to the spiral bevel gear, which is the bevel counterpart of the helical gear. As in the case of helical gears, spiral bevel gears give a much smoother tooth action than straight bevel gears, and hence are useful where high speed are encountered. It is frequently desirable, as in the case of automotive differential applications, to have gearing similar to bevel gears but with the shaft offset. Such gears are called hypoid gears because their pitch surfaces are hyperboloids of revolution. The tooth action between such gears is a combination of rolling and sliding along a straight line and has much in common with that of wormgears.A shaft is a rotating or stationary member, usually of circular cross section, having mounted upon it such elements as gears, pulleys, flywheels, cranks, sprockets, and other power-transmission elements. Shaft may be subjected to bending, tension, compression, or tensional loads, acting singly or in combination with one another. When they are combined, one may expect to find both static and fatigue strength to be important design considerations, since a single shaft may be subjected to static stresses, completely reversed, and repeated stresses, all acting at the same time.The word “shaft〞 covers numerous variations, such as axles and spindles. An axle is a shaft, wither stationary or rotating, nor subjected to torsion load.A shirt rotating shaft is often called a spindle.When either the lateral or the tensional deflection of a shaft must be held to close limits, the shaft must be sized on the basis of deflection before analyzing the stresses. The reason for this is that, if the shaft is made stiff enough so that the deflection is not too large, it is probable that the resulting stresses will be safe. But by no means should the designer assume that they are safe,it is almost always necessary to calculate them so that he knows they are within acceptable limits. Whenever possible, the power-transmission elements,such as gears or pullets, should be located close to the supporting bearings, This reduces the bending moment, and hence the deflection and bending stress.Although the von Mises-Hencky-Goodman method is difficult to use in design of shaft, it probably comes closest to predicting actual failure. Thus it is a good way of checking a shaft that has already been designed or of discovering why a particular shaft has failed in service. Furthermore, there are a considerable number of shaft-design problems in which the dimension are pretty well limited by other considerations, such as rigidity, and it is only necessary for the designer to discover something about the fillet sizes, heat-treatment, and surface finish and whether or not shot preening is necessary in order to achieve the required life and reliability.Because of the similarity of their functions, clutches and brakes are treated together. In a simplified dynamic representation of a friction clutch, or brake, two inertias I1 and I2 traveling at the respective angular velocities W1 and W2, one of which may be zero in the case of brake, are to be brought to the same speed by engaging the clutch or brake. Slippage occurs because the two elements are running at different speeds and energy is dissipated during actuation, resulting in a temperature rise. In analyzing the performance of these devices we shall be interested in the actuating force, the torque transmitted, the energy loss and the temperature rise. The torque transmitted is related to the actuating force, the coefficient of friction, and the geometry of the clutch or brake. This is problem in static, which will have to be studied separately for earth geometric configuration. However, temperature rise is related to energy loss and can be studied without regard to the type of brake or clutch because the geometry of interest is the heat-dissipating surfaces. The various types of clutches and brakes may be classified as fellows.1.Rim type with internally expanding shoes2.Rim type with externally contracting shoes3.Band type4.Disk or axial type5.Cone type6.Miscellaneous typeThe analysis of all type of friction clutches and brakes use the same general procedure. The following step are necessary:1.Assume or determine the distribution of pressure on the frictional surfaces.2.Find a relation between the maximum pressure and the pressure at any point.3. Apply the condition of statically equilibrium to find (a) the actuating force, (b) the torque, and (c) the support reactions.Miscellaneous clutches include several types, such as the positive-contact clutches, overload-release clutches, overrunning clutches, magnetic fluid clutches, and others. A positive-contact clutch consists of a shift lever and two jaws. The greatest differences between the various types of positive clutches are concerned with the design of the jaws. To provide a longer period of time for shift action during engagement, the jaws may be ratchet-shaped, or gear-tooth-shaped. Sometimes a great many teeth or jaws are used, and they may be cut either circumferentially, so that they engage by cylindrical mating, or on the faces of the mating elements.Although positive clutches are not used to the extent of the frictional-contact type, they do have important applications where synchronous operation is required. Devices such as linear drives or motor-operated screw drivers must run to definite limit and then come to a stop. An overload-release type of clutch is required for these applications. These clutches are usually spring-loaded so as to release at a predetermined toque. The clicking sound which is heard when the overload point is reached is considered to be a desirable signal.An overrunning clutch or coupling permits the driven member of a machine to “freewheel〞or “overrun〞 because the driver is stopped or because another source of power increase the speed of the driven. This type of clutch usually uses rollers or balls mounted between an outer sieve and an inner member havingflats machined around the periphery. Driving action is obtained by wedging the rollers between the sleeve and the flats. The clutch is obtained by wedging the rollers between the sleeve and the flats. The clutch is therefore equivalent to a pawl and ratchet with an infinite number of teeth.Magnetic fluid clutch or brake is a relatively new development which has two parallel magnetic plates. Between these plates is a lubricated magnetic powder mixture. An electromagnetic coil is inserted somewhere in the magnetic circuit. By varying the excitation to this coil, the shearing strength of the magnetic fluid mixture may be accurately controlled. Thus any condition from a full slip to a frozen lockup may be obtained .齿轮和轴的介绍减速器是一种动力传达机构，利用齿轮的速度转换器，将马达的回转数减速到所要的回转数，并得到较大转矩的机构。

双电机驱动双曲柄四环板针摆行星减速器参数化设计的开题报告

双电机驱动双曲柄四环板针摆行星减速器参数化设计的开题报告一、选题背景和意义随着现代工业的不断发展，各行各业对于减速器的需求越来越高。

在机械传动中，减速器的作用是将高速低扭力的动力通过减速器转化成低速高扭力的动力输出。

其中，行星减速器作为一种常见的机械传动装置，因其具有结构紧凑、扭矩传递可靠、传动效率高等特点，在工业生产中得到了广泛应用。

而在行星减速器领域中，四环板针摆行星减速器因其结构简单、可靠性高、扭矩传递平稳等优点，逐渐成为行星减速器的主流结构之一。

双曲柄四环板针摆行星减速器则更是在设计中降低了轴向载荷，增加了传动效率等优点，因此应用广泛。

本论文拟以双电机驱动双曲柄四环板针摆行星减速器为研究对象，着重分析该减速器的传动性能和运动特点，并通过参数化设计的方法进行研究，最终实现该减速器的合理优化设计，以满足现代制造业对于行星减速器性能不断提升的需求。

二、研究内容和技术路线本论文将以双电机驱动双曲柄四环板针摆行星减速器为研究对象，通过参数化设计的方法，对其结构参数进行优化设计，以实现减速器传动性能的提高和运动特性的改善。

具体的研究内容包括：1. 双曲柄四环板针摆行星减速器的结构分析：通过对双曲柄四环板针摆行星减速器的结构分析，得出其传动和运动特点，并研究影响其传动性能和运动特性的主要结构参数。

2. 研究双电机驱动的针摆行星减速器受力分析：将双电机驱动双曲柄四环板针摆行星减速器作为一个整体进行受力分析，分析其在工作过程中的受力情况。

3. 参数化设计：根据分析结果对双曲柄四环板针摆行星减速器的结构参数进行参数化设计，以实现减速器的优化设计。

参考技术路线：1. 参考基于有限元分析的针摆行星减速器受力分析方法，建立减速器模型，进行有限元分析，分析针摆行星减速器的受力情况。

2. 结合减速器的受力情况，使用参数化设计的软件（如SolidWorks等），对减速器的结构参数进行参数化设计，以实现减速器的合理优化设计。